Change-speed mechanism fob machine tools



W. T. EMMES CHANGE SPEED MECHANISM FOR MACHINE TOOLS Nov. 9, 1926. 1,605,931

Filed April 16. 1924 9 sheetkshet 1 HANDLES INVEMR Nov. 9 1926.

W. T. EMMES CI'IMJGEv SPEED MECHANISM FOR' MACHINE TOOLS Filed April 16. 1924 9 sheets sheet 2 Nov. 9 l926.' 1,605,931

w. 'r. EMMES CHANGE SPEED MECHANISM FOR MACHINE TOOLS Filed April 16 1924 9 Sheets-Sheet a 27' ii k 6- 74;? s2 78 I 54' i 1 [T l I v 28 29 7 Nev. 9, 1926. 1,605,931

W. T. EMMES CHANGE SPEED MECHANISM FOR MACHINE TOOLS Filed April 16. 1924 9 Sheets-Sheet 4 136. 8 I gffia -51 as 35' K 33 NVEMOR Nbv. 9 1926. 1,605,931

W. T. EMMES CHANGE SPEED MECHANISM FOR MACHINE TOOLS Filed April 1.924 9 Sheets-Sheet 5 TREJQ INVEN tom Nov. 9 1926, 1,605,931

w. 'r. EMMES CHANGE SPEED MECHANISM FOR MACHINE TQQLS Filed April 16, 1924 9 s t sh t 6 55' 3: 35 '58 a i K6 {2 UWEMQR Nov. 9, 1926. 1,605,931

W. -T. EMMES CHANGE SPEED MECHANISM FOR MACHINE TOOLS Filed April 16. 1924 s t sh t 7 Sew Nov. 9, 1926. 1,605,931

W. T. EMMES CHANGE SPEED MECHANISM FOR MACHINE TOOLS Filed April 16. 1924 9 sheets 5heet, 3

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W. T. EMMES QHANGE SPEED MECHANISM? FOR MACHINE TOOLS Filed April 16. 1924 1 9 sheetsheei 9 F lG- 1'1 (NEW R Fatented New. Q, 132%.

pie-i- VJILLZIAIII T. EMMEEi, F CINCINNATI, OHIO.

CHANGE-SPEED MECHANISM FOR MACHINE TOGLS.

Application filed April 16, 1924. Serial No. 707,004.

This invention has for an object'to prouce a change speed device which is parcularly designed for lathe constructions, but which may be as readily embodied in the construction of milling machines, boring machines or other machines and machine tools,

a. further object is to produce a change speed mechanism in which relatively small, compact and simple parts are employed and in which these elements are so disposed relatively to one another, that they are readily accessible for purposes of repair, etc.

A further object is to produce a change speed mechanism in which a maximum number of speed changes are obtainable with a minimum number of parts.

A. further object is to produce a change speed mechanism in which a minimum num- 'ber of operations are necessary to obtain a maximum number of speed changes.

These and other objects are attained in the change speed mechanism described in the following specification and illustrated in the accompanying drawings, in which Fig. 1 is a plan view of my improved change speed construction, parts being shown in section andother parts. in elevation for convenience of illustration.

Fig. 2 is an end elevation of the casing enclosing my improved change speed mechanism.

Fig. 3 is a transverse sectional view taken on the line 33 of Fig. 1. V

Fig. 4 is a transverse sectional view taken on the line 44 of Fig. 1.

Fig. is a longitudinal sectional view of the portion of the mechanism designated by line 55 in Fig. 1.

Fig. 6 is a view of a direction chart or table which is employed in directing the operator of the machine tool as to the correct manner in manipulating the handles which control the shifting of the gears to obtain the various speed changes to be obtained by my improved mechanism.

Figs. 7 to 18 inclusive disclose in diagrammatic manner the positions of the gears, clutches and other objects of the mechanism, relatively to one another, in

order toproduce the several speed changes which are. obtainable by means of my improved construction.

in my improved change speed mechanism I have disclosed, in Fig. 1, a casing 27 which .and'40 are gear 41 and a pinion 42. gear and pinion are rotatably mounted independently upon shaft 30. Gears 39 and '41 are provided with the respective clutch encloses all the elements of the speed change portion of my invention. lVithin the casing suitable bearings mount a drive shaft 28, a work-carrying spindle 29, a primary intermediate shaft 30 and a secondary iiitermediate shaft 31. R-otatively mounted -upon shaft 28 are two pinions 32 and 33,

.member 34 is moved toward pinion Thus either pinion 32 or pinion 33 may be driven from clutch member 34 because of its splined connection with drive shaft 23.

Primary intermediate shaft 30 carries two gears 39 and 40 which are keyed thereto and which mesh continuously with pinions 32 and respectively. Between gears 39 This teeth 43 and 44 which are adapted to engage 'upon movement of gear 41 toward gear 39.

Gear 40 and pinion 42 are provided with the respective clutch teeth 45 and 46 which will engage when pinion 42 is moved toward gear 40. Although gear 41 and pinion 42 are independent of each other, it is necessary that they be moved longitudinally of shaft 30 simultaneously, in order that clutch. teeth 4344.and clutch teeth 4546 will not be engaged simultaneously. To accomplish this I have. provided a sliding bar 47, (see Figure 5) which is provided with embracing yoke 48. In order to limit the movement of this bar 47 I have provided a pin 49 which slides in a slot 50 in the mounting frame 51 which carries bar 47. This pin 49 extends above frame 51 in order that the bar may be operated from suitable instrumentality which will be described hereinafter. Adjacent to bar 47 T have provided another bar 52, (see Fig. 4,) which is mounted in the same manner as bar 47 and which is provided with a pin 53, (see Fig.

1,) for causing reciprocationin the same manner as bar 47. This bar 52 is provided with a finger 5 4, (see. F 1g. 4,) which grasps a flange 55 on clutch member'34, so that-the clutch member may be!v reciprocated. As with pin 49, suitable instrumentalities which will also be described hereinafter, have been provided for effecting reciprocation of bar 52 in cooperation with its operating pin 53.

\Vork-carrying spindle 29, (see Fig. 1,) which lies next adjacent to shaft 30, carries a pinion 56 which is rotatably mounted on the spindle and which is provided with an elongated hub 57 having clutch teeth 58 at its end. Keyed to hub 57 are the united pinion 59 and gear 60, these .1nesh ing with gear 41 and pinion 42 respectively. Adjacent to teeth 58 is a clutch member 61 which is splined to spindle 29 and which carries clutch teeth 62 at oneqend for cooperationwith teeth 58, teeth 63 being formed at the opposite end for cooperation with teeth 64 upon a gear 65 which is rotatably mounted on the spindle. Thus when clutch .member 61 is moved either to the right or to the left, it will engage its teeth 63 and 62 with the cooperating teeth 64 and 58 respectively, so that the spindle will be driven either from gear 65 or pinion 56 as will be hereinafter more fully described. The manner and means of operation of clutch member 61 will also be described hereinafter.

Secondary intermediate shaft 31, which lies next adjacent to spindle 29, carries a rotatably mounted gear 66 which meshes continuously with pinion 56 on spindle 29. In addition to this another mounted gear 67 is provided. This gear meshes with gear 60 on hub 57 carried by spindle 29. Between gears 66 and 67 a clutch member 68, which is splined to shaft 31, is located. This member 68 is provided with clutch teeth 69 and 70, these teeth engaging the respective teeth 71 and 72 formed on the respective gears 66 and 67. Thus when member 68 is shifted to either of its extreme positions it will unite either of the gears 66 or 67 with shaft 31 for driving purposes. Adjacent to the opposite end of shaft 31 I have provided a pinion '73 which is keyed to the shaft and which meshes continuously with gear 65. I will now describe the means by which the shifting of clutch members 34, 61, and 68, as well as of gear 41 and pinion 42,is accomplished. Engaging pin 53 is a lever 74, (see Fig. 3,) the hub 75 of which extends through casing 27 and has attached thereto an operating handle B, (see Fig. 2,) engag ing pin 49 is a lever 76, (see Fig. 3,) the shaft 77 of which passes thr-u hub 75 and has attached thereto an operating lever A, ($.68 Fig. 2,). In order to operate clutch member 68, (see Fig. 1,) I have rovided a finger 78 which enga s an annu' ar groove 79 in the clutch mean er. The fin er 78 is mounted in a short lever .80, (seeFig. 4,) attached to a shaft 81 extending through pinion 56.

the side of .a casing 27 and to the outer end of which an operating lever D is attached. This lever when shifted to the right and then to the left, will bring clutch teeth 7270, (see Fig. 1.) and 7l69 into alternate engagement. For retaining lever I), in either position designed to accomplish this, I have provided a ball and socket lever retaining device 82, (see Fig. 4,). The means for shifting clutch member 61 is identical with that for shifting member 68 and consists of a finger 83 which engages annular groove 84 of member 61, finger 83 being mounted upon lever 85, (see Fig. 3,) which is attached to shaft 86 which extends throughcasing 27 and is provided at its outer end with an operating lever C, (see Fig.

2,). Like lever D, lever C, is provided with a ball and socket lever retaining device 87, (see Fig. 3,) in order that member 61, when the lever C, is moved to one or the other of its positions, may retain teeth 58-62 or 63.64 in engagement. I have provided bars 47 and 52 with a ball and socket bar retaining device 88, (see Fig. 5,) which, like devices 82 and 87, operates to retain clutch member 34. (see Fig. 1,) in either of its shifted positions or to retain gear 41 and pinion 42 in either of their shifting positions. In each of these ball and socket devices 82, 87 and 88, the levers A, B, C, and D, are arranged for retention in neutral position, so that, the clutch teeth of none of their connected elements will engage. By this means and the shifting of the various clutches into one or the other of their several operative positions, the several speed changes, which I have indicated in Fig. 6, and which will be described hereinafter, will be accomplished.

The manner in which the several speed changes to be obtained by the mechanism I have disclosed in Fig. 1, is accomplished. will now be described, reference being had to Figs. 7 to 18 inclusive during such de' scription, each of the figures showing how the shifting of the clutch members will accom' plish the several speed changes indicated and shown in the direction table disclosed in F ig. 6 thereof. I have chosen to start my description with Fig. 7 in which elements of the mechanism are shown in the position they will occupy to produce a spindle speed of nine revolutions a minute. To produce this, spindle clutch member 34'is shifted so that teeth 35 and36 will engage. By this means pinion 32, gear 39 and shaft 30 are rotated. Pinion 42 is shifted to bringteeth 45 and 46 into engagement and thus to drive pinion 42 and its gear 60 which also drives Shaft 31 is-then operatively connected with gear 66 by shifting clutch member 68 so that teeth 69 and 71 will engage. Thus shaft 3 1 will .glrive pinion 73 and its cooperating gear 65. Spindle 29 is 110w iii] connected with gear 65 by moving clutch member 61 so that teeth 63 and 64 will engage. This will be accomplished by moving handles A, B, C, and D, to the left, right, right and left respectively as indicated in the direction table of Fig. 6, and when standing in front of the operating front of a machine, inch is the left hand 'ide of Figs. 2, 3, and 4.

The next speed change to a spindle speed of 13 revolutions to the minute, Fig. 8, will be accomplished by shifting clutch member 34 to the right, so that teeth 37 and 38 en Pinion 42 is then shifted to the right, so that teeth 45 and 46 engage. Clutch member 63 is also shifted, so that teeth 69 and 71 engage. Clutch member 61 is then shifted, so that teeth 63 and 64 engage. Thus the only difference between the setting to produce 13 revolutions per minute as distinguished from 9 revolutions per minute, is in the position of clutch member 34 which is just the reverse of that previously described.

In Fig. 9, I have shown the setting required to produce a spindle speed of 18 revolutions per minute. This is accomplished by the mere shifting of clutch member 34 to bring teeth 35 and 36 into engagement and by merely shifting gear 41 and pinion 42 so that teeth 45 and 46 are disengaged and teeth 43 and are brought into engagement with each other. The clutch members 61 and 68 are allowed to remain in the positions they occupied during the two speed changes previously described.

In Fig. 10, I have shown the setting re quired to produce a spindle speed of 24 revolutions per minute. This setting is identical with that shown in Fig. 9 except for the shifting of member 34 to bring teeth 37 and into engagement.

Tn bringing about aspindle speed of revolutions a minute, Fig. 11, clutch members 34 and 68 are now shifted to engage teeth and 36, as well as teeth 70 and 72, gear 41 and pinion 42 being shifted to bring teeth and 46 into engagement.

In 12, a spindle speed of 43 revolutions a minute is brought about, by merely shifting clutch member 34, from its position disclosed in Fig. 11, so that, teeth 37 and 38 are brought into engagement. The remaining shiftable members are allowed to remain in the positions they occupy in producing the spindle speed of 30 revolutions per minute.

In Fig. 13, a speed of revolutions per minute, will be imparted to the spindle, by merely shifting clutch member 34 and gear 41 with pinion 42. This change, from that disclosed in Fig. 12, brings teeth 35 and 36 as well as teeth 43 and 44 into engagement.

in Fig. 14, by now merely shifting clutch member 34, to bring teeth 37 and 38 into engagement, I accomplish a change in spindle speed from 60 to revolutions a minute.

Fig. 15, discloses the positions occupied by the shiftable member in order to produce a spindle speed of revolutions a minute. This is accomplished by now shifting member 34 to bring teeth 35 and 36 into engagement, by shifting gear 41 and pinion to bring teeth 45 and 46 into engagen'ient, by shifting clutch member 61, to bring teeth 58 and 62 into engagement and by shifting clutch member (38 to free both gears 66 and 6'7. Thus the spindle is driven directly from pinion 42, driving thru gear 60 and splined clutch member 61 onto the spindle.

The next step-up in speed change is to 175 revolutions a minute, Fig. 16, and is accomplished, by merely shifting clutch member 34 from the position shown in Fig. 15, so that teeth 3'? and 38 will engage.

In Fig 17, the shifting of clutch member 34 and gear 41 with pinion 42 in order that teeth 3536 and teeth 4344 may be engaged, will accomplish a speed change in which the spindle is driven at 250 revolutions a minute.

in Fig. 18, the final increase in speed transmitted to the spindle, is accomplished *y merely shifting member 34, so that its teeth 37 and 38 engage. This speed is 350 revolutions a minute.

Having thus described my invention what I claim is:

1. A change speed mechanism comprising a drive shaft, a primary intermediate shaft, a secondary intermediate shaft, a work spindle, and a series of constantly meshing gears on the shafts and spindle, the gears on the primary intermediate shaft consisting of a pair of gears spaced apart and keyed to the shaft, and a pair of gears mounted on the shaft and having longitudinal shifting movement and independent rotation thereon, each of said keyed gears having clutch teeth on the sides thereof facing the rota tively mounted gears, each of said rotatively mounted gears having clutch teeth on the side thereof adjacent to and for cooperation with the clutch teeth of the keyed gears, and a yoke embracing the faces of the independently rotatable gears, adapted to effect longitudinal movement of the rotatively mounted gears as a unit toward or away from one or the other of the keyed gears, whereby engagement or disengagement of the sets of clutch teeth may be brought about, the gears on the drive shaft constant ly meshing with the keyed gears on the primary intermediate shaft, and certain of the gears on the spindle constantly meshing with the longitudinally shiftable independently rotatable gears of the primary inter mediate shaft.

2. A change speed mechanism comprising 7 pair of gears spaced apart and keyed to the shaft, and a pair of gears mounted on the shaft and having longitudinal shifting movement and independent rotation thereon, each of said keyed gears having clutch teeth on the side thereof facing the rotatively mounted gears, each of said rotatively mounted gears having clutch teeth on the side thereof adjacent to and for cooperation with the clutch teeth of the keyed gears,

and a yoke embracing the faces of the independently rotatable gears, adapted to effect longitudinal movement of the rotatively mounted gears as a unit toward or away from one or the other of the keyed gears, whereby engagement or disengagement or the sets of clutch teeth may be brought about, the gearson the drive shaft constant ly meshing with the keyed gears on the primary intermediate shaft, and certain of the gears on the spindle constantly meshing with the longitudinally shiftable independently rotatable gears of the primary intermediate shaft, the gears of each intermeshing pair of gears being of a different speed ratio than any other of said pairs of intermeshing gears.

In Witness whereof, I affix my signature.

'WILLIAM T. EMMES. 

